CN102997527A - Gas-liquid heat exchange type refrigeration device - Google Patents
Gas-liquid heat exchange type refrigeration device Download PDFInfo
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- CN102997527A CN102997527A CN2011102813135A CN201110281313A CN102997527A CN 102997527 A CN102997527 A CN 102997527A CN 2011102813135 A CN2011102813135 A CN 2011102813135A CN 201110281313 A CN201110281313 A CN 201110281313A CN 102997527 A CN102997527 A CN 102997527A
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- 239000007788 liquid Substances 0.000 title claims abstract description 112
- 238000005057 refrigeration Methods 0.000 title abstract description 5
- 239000003507 refrigerant Substances 0.000 claims description 148
- 238000004804 winding Methods 0.000 claims description 25
- 238000001704 evaporation Methods 0.000 claims description 17
- 230000008020 evaporation Effects 0.000 claims description 14
- 238000004781 supercooling Methods 0.000 claims description 12
- 230000005494 condensation Effects 0.000 claims description 6
- 238000009833 condensation Methods 0.000 claims description 6
- 239000002826 coolant Substances 0.000 abstract description 19
- 230000007306 turnover Effects 0.000 abstract 1
- 238000000034 method Methods 0.000 description 21
- 230000008569 process Effects 0.000 description 18
- 230000008859 change Effects 0.000 description 9
- 230000006837 decompression Effects 0.000 description 8
- 230000000630 rising effect Effects 0.000 description 6
- 238000010586 diagram Methods 0.000 description 5
- 238000001816 cooling Methods 0.000 description 4
- 238000009835 boiling Methods 0.000 description 3
- 230000006835 compression Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 3
- 230000007812 deficiency Effects 0.000 description 3
- 230000009467 reduction Effects 0.000 description 3
- 230000005514 two-phase flow Effects 0.000 description 3
- 238000004378 air conditioning Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000008676 import Effects 0.000 description 2
- 238000004088 simulation Methods 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000033228 biological regulation Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000007710 freezing Methods 0.000 description 1
- 230000008014 freezing Effects 0.000 description 1
- 230000005764 inhibitory process Effects 0.000 description 1
- 230000007115 recruitment Effects 0.000 description 1
- 238000004544 sputter deposition Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
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Abstract
The invention discloses a gas-liquid heat exchange type refrigeration device. Refrigeration capability variations caused by the variations of the turnover number of a compressor can be suppressed, and the rise of discharge temperature at an outlet of the compressor can be suppressed to prevent refrigerator oil from being degraded. The liquid-gas heat exchange type refrigeration device consists of the compressor 1, a condenser 2, a heat exchange control valve 3, a gas-liquid heat exchanger 4, an expansion valve 5 and an evaporator 6, which are connected in series through a coolant pipeline to form a closed coolant circulation pipeline. A discharge temperature sensor 7 is arranged between the compressor 1 and the condenser 2 of the coolant circulation loop. A pressure sensor 8 is arranged between the heat exchange control valve 3 and the gas-liquid heat exchanger 4. A controller (control device) 10 is also arranged to control the opening of the heat exchange control valve 3 on the basis of coolant temperature detected by the discharge temperature sensor 7 at the outlet of the compressor 1 and coolant pressure detected by the pressure sensor 8 at an outlet of the heat exchange control valve 3.
Description
Technical field
The present invention relates to a kind of gas-liquid heat exchange type refrigerating plant, its will be by condenser condenses refrigerant and by evaporator evaporation refrigerant, in gas-liquid heat exchanger, carry out mutually heat exchange, make the respectively supercooling and overheated of each refrigerant, improve thus refrigerating capacity.
Background technology
In general, refrigerating plant, by refrigerant pipeline compressor, condenser, expansion valve and the connection of evaporator series ground to be consisted of closed circuit refrigerant circulation circuit, by compressor compresses the gaseous coolant of high pressure, heat release in condenser and liquefying, become the liquid refrigerants of high pressure, this liquid refrigerants is expanded (isenthalpic expansion) and after the decompression by expansion valve, in evaporimeter, make the low-pressure liquid refrigerant evaporation after boiling point descends, according to capturing the needed evaporation latent heat of evaporation from inner grade of freezer, cool off the places such as freezer inside.
As the refrigerating capacity that improves this kind refrigerating plant or the method for coefficient of refrigerating performance (COP), known have such method, described method is between the evaporimeter of refrigerant circulation circuit and expansion valve gas-liquid heat exchanger to be set, and make by the refrigerant after the condenser condenses and by the refrigerant after the evaporator evaporation, in gas-liquid heat exchanger, carry out mutually heat exchange, and make the respectively supercooling and overheated of each refrigerant.
In addition, in patent documentation 1, for the refrigerating air-conditioning that is equiped with gas-liquid heat exchanger, propose such as lower device, described device is between the condenser of refrigerant circulation circuit and the gas-liquid heat exchanger and between gas-liquid heat exchanger and the evaporimeter, expansion valve is set respectively, and control the aperture of expansion valve based on the refrigerant temperature of the refrigerant temperature of condensator outlet and suction port of compressor, the desired value that remains on regulation by the mass dryness fraction with the refrigerant at evaporator outlet place realizes high efficiency running, and eliminates and result from that evaporimeter becomes dry and the unfavorable condition of the condensed water sputtering that causes etc.
The prior art document
Patent documentation
Patent documentation 1: TOHKEMY 2009-162388 communique
Invent problem to be solved
Yet, if under the environment that the winding number meeting of the compressor as van cooler changes significantly, the situation that the refrigerating air-conditioning that patent documentation 1 is proposed turns round, then the heat exchange performance of gas-liquid heat exchanger also can be followed the winding number change of compressor and change significantly.For example, refrigerant circulation reduces if the winding number of compressor reduces then, cause that owing to the heat exchange amount in gas-liquid heat exchanger is not enough cooling occurs bad, on the contrary, if the winding number increase of compressor then refrigerant circulation increases, the temperature that spues of too much causing the refrigerant at compressor outlet place owing to heat exchange amount rises, and the problem of the deteriorated grade of refrigerator oil occurs.
The present invention finishes in view of the above problems, its purpose is to provide a kind of gas-liquid heat exchange type refrigerating plant, it can suppress to follow the change of winding number of compressor and the change of the refrigerating capacity that causes, and the rising of the temperature that spues at inhibition compressor outlet place, and it is deteriorated to prevent that refrigerator oil from occuring.
Summary of the invention
The technological means of dealing with problems
To achieve these goals, the invention of technical scheme 1, it is a kind of gas-liquid heat exchange type refrigerating plant, by refrigerant pipeline, to major general's compressor, condenser, the heat exchange control valve, gas-liquid heat exchanger, expansion valve and evaporimeter, be connected in series, and consist of closed circuit refrigerant circulation circuit, the refrigerant that will be in aforementioned condenser have been reduced pressure by aforementioned hot exchange control valve after the condensation and by vaporized refrigerant in the aforementioned evaporation device, in aforementioned gas-liquid heat exchanger, carry out heat exchange and make the respectively supercooling or overheated of each refrigerant, it is characterized in that: between the aforementioned compressor and aforementioned condenser of aforementioned refrigerant circulation circuit, the setting temperature sensor that spues, and between aforementioned hot exchange control valve and aforementioned gas-liquid heat exchanger, pressure sensor is set, and be provided with control device, described control device is controlled the aperture of aforementioned hot exchange control valve based on refrigerant temperature and the refrigerant pressure that is exported by the detected heat exchange control valve of aforementioned pressure sensor by the aforementioned detected compressor outlet of temperature sensor that spues.
The invention of technical scheme 2, be based on technical scheme 1 described invention, it is characterized in that: aforementioned control device, if the winding number of aforementioned compressor reduces the aperture of then dwindling aforementioned hot exchange control valve, if the winding number of aforementioned compressor increases, then increase the aperture of aforementioned hot exchange control valve.
The invention of technical scheme 3, be based on technical scheme 1 described invention, it is characterized in that: aforementioned control device, if the refrigerant temperature by the aforementioned detected compressor outlet of temperature sensor that spues surpasses setting value, the aperture that then aforementioned hot is exchanged control valve is contracted to till the value that can make refrigerant maintain the gas-liquid mixed state, and described refrigerant is the refrigerant that has passed through aforementioned gas-liquid heat exchanger after being reduced pressure by this heat exchange control valve.
The effect of invention
According to technical scheme 1 and technical scheme 2 described inventions, because the aperture of when the rotation number of compressor reduces, dwindling the heat exchange control valve, so flowing through the flow velocity of the refrigerant of gas-liquid heat exchanger rises, heat exchange amount increases, and according to the increase of this heat exchange amount, can compensate the minimizing that reduces the heat exchange amount in gas-liquid heat exchanger that the minimizing cause refrigerant circulation causes because of winding number, and it is bad to suppress the cooling that causes because of the heat exchange amount deficiency.
In addition, owing to when the rotation number of compressor increases, increasing the aperture of heat exchange control valve, so flowing through the flow velocity of the refrigerant of gas-liquid heat exchanger descends, heat exchange amount reduces, and according to the minimizing of this heat exchange amount, the increase that increases the heat exchange amount in gas-liquid heat exchanger that the increase cause refrigerant circulation causes because of winding number can be compensated, the rising of the temperature that spues of refrigerant in the exit of the compressor that too much causes because of heat exchange amount can be suppressed.
According to technical scheme 3 described inventions, because when the refrigerant temperature of compressor outlet surpasses setting value, dwindle significantly the aperture of heat exchange control valve 3, so that till maintaining the value of gas-liquid mixed state by the refrigerant that has passed through gas-liquid heat exchanger after the heat exchange control valve decompression, therefore with the form of gas-liquid two-phase flow by the refrigerant of gas-liquid heat exchanger and come the temperature difference between the gaseous coolant of flash-pot to diminish, so the heat exchange amount of two refrigerants in gas-liquid heat exchanger can be suppressed to lower.Therefore, the degree of superheat of the refrigerant at suction port of compressor place can be suppressed to lower, and can suppress the rising of the temperature that spues of the refrigerant at compressor outlet place, and can prevent the deteriorated of refrigerator oil.
Description of drawings
Fig. 1 is the refrigerant loop diagram of gas-liquid heat exchange type refrigerating plant of the present invention.
Fig. 2 is illustrated in the gas-liquid heat exchange type refrigerating plant of the present invention, the mollier diagram of the state variation of the refrigerant the when aperture of heat exchange control valve is controlled in the change of corresponding compressor winding number.
Fig. 3 is illustrated in the flow velocity of the condensate liquid refrigerant in the gas-liquid heat exchanger and the graph of a relation of heat transfer property.
Fig. 4 is illustrated in the gas-liquid heat exchange type refrigerating plant of the present invention, when the temperature that spues of the refrigerant at compressor outlet place surpasses setting value, and the mollier diagram of the state variation of the refrigerant when having controlled the aperture of heat exchange control valve.
The critical piece symbol description
1 compressor
2 condensers
3 heat exchange control valves
4 gas-liquid heat exchangers
5 expansion valves
6 evaporimeters
7 temperature sensors that spue
8 pressure sensors
9 evaporating temperature sensors
10 controllers (control device)
Refrigerant pipeline
The specific embodiment
Below, with reference to accompanying drawing example of the present invention is described.
Fig. 1 is the refrigerant loop diagram of gas-liquid heat exchange type refrigerating plant of the present invention, in illustrated gas-liquid heat exchange type refrigerating plant, compressor 1, condenser 2, heat exchange control valve 3, gas-liquid heat exchanger 4, expansion valve 5 and evaporimeter 6, be connected in series by refrigerant pipeline L1, L2, L3, L4, L5, and formed closed circuit refrigerant circulation circuit.Herein, heat exchange control valve 3 is arranged on the refrigerant pipeline L2, and described refrigerant pipeline L2 is in order to connect condenser 2 and gas-liquid heat exchanger 4; Expansion valve 5 is arranged on the refrigerant pipeline L3, and described refrigerant pipeline L3 is in order to connect gas-liquid heat exchanger 4 and evaporimeter 6.In addition, heat exchange control valve 3 is made of the electronic control valve of controlling aperture in stepless mode.
In addition, in gas-liquid heat exchange type refrigerating plant of the present invention, the temperature sensor 7 that spues is arranged on to connect on the refrigerant pipeline L1 of compressor 1 and condenser 2, pressure sensor 8 is arranged on the refrigerant pipeline L2 between heat exchange control valve 3 and the gas-liquid heat exchanger 4,9 of evaporating temperature sensors are arranged on to connect on the refrigerant pipeline L4 of evaporimeter 6 and gas-liquid heat exchanger 4, these temperature sensors 7 that spue, pressure sensor 8 and evaporating temperature sensor 9, being electrically connected to control device is on the controller 10.And then the heat exchange control valve 3 by electronic control valve consists of is electrically connected to controller 10, and as described later, heat exchange control valve 3 is according to coming the control signal of self-controller 10 to control its aperture.
Then, use mollier diagram (P-i line chart) shown in Figure 2 to come the Action Specification of gas-liquid heat exchange type refrigerating plant of the present invention as follows.
If compressor 1 is not shown engine and being driven by revolution according to drive source, then be positioned at the state (pressure P shown in a of Fig. 2
1, enthalpy i
1) gaseous coolant by compressor 1 compression, become the state (pressure P shown in the b of Fig. 2
2, enthalpy i
2) the gaseous coolant (compression travel) of HTHP, this gaseous coolant is imported in the condenser 2 by refrigerant pipeline L1.In addition, the compression power W (being converted into heat) of the compressor 1 of this moment is with (i
2-i
1) represent.
In condenser 2, the gaseous coolant of HTHP is with condensation heat Q
2Be discarded in the atmosphere, become the state (phase change) at c place and liquefy (condensation stroke) becomes the state (pressure P shown in the c of Fig. 2 by the state variation at the b place of Fig. 2
2, enthalpy i
3) the high-pressure liquid refrigerant.In addition, thermal discharge (condensation heat) Q of this moment
2With (i
2-i
3) represent.
Then, as described above, the high-pressure liquid refrigerant that has liquefied in condenser 2 in Fig. 2, for example carries out state variation through the path (condition) that represents with B.That is, the high-pressure liquid refrigerant that has liquefied in condenser 2 arrives heat exchange control valve 3 by refrigerant pipeline L2, by this heat exchange control valve 3, is depressurized to pressure P
3Till carry out adiabatic expansion (isenthalpic expansion) (expansion stroke), become the state (pressure P shown in the d of Fig. 2
3, enthalpy i
3), its a part of refrigerant can gasify.
As described above, the refrigerant that a part has gasified, can be imported in the gas-liquid heat exchanger 4 by refrigerant pipeline L2, in this gas-liquid heat exchanger 4, as described later, evaporation in evaporimeter 6 and the gaseous coolant that gasified are through refrigerant pipeline L4 and be imported into, so refrigerant that imports from refrigerant pipeline L2 and toward gas-liquid heat exchanger 4 (part gasify refrigerant), the gaseous coolant of the low temperature that can be with evaporation in evaporimeter 6 imports from refrigerant pipeline L4 carries out heat exchange and by supercooling, becomes the state (pressure P shown in the e of Fig. 2
3, enthalpy i
4) liquid refrigerants.In addition, the supercooling heat Δ Q of this moment
2With (i
3-i
4) represent.
Then, as described above, by the refrigerant after the supercooling, according to again reduced pressure to carry out adiabatic expansion (isenthalpic expansion) (expansion stroke) by expansion valve 5, state variation becomes the state (pressure P shown in the f of Fig. 2 in gas-liquid heat exchanger 4
1, enthalpy i
4), so its a part of refrigerant can gasify, and reduce boiling point because of decompression.So, be depressurized by expansion valve 5 and the refrigerant of boiling point after reducing, be directed into evaporimeter 6 from refrigerant pipeline L3, in the process that flows through this evaporimeter 6, this refrigerant can from around capture heat of evaporation Q
1And evaporate, the state variation shown in the f becomes the state (pressure P shown in the g
1, enthalpy i
5) and gasify (evaporation stroke).The heat of evaporation Q of this moment
1With (i
5-i
4) represent, but as described above, be inflated the front refrigerant of valve 5 decompressions, in gas-liquid heat exchanger 4, only can be by supercooling Δ Q
2(=i
3-i
4), so heat of evaporation only can increase the heat Δ Q of this supercooling amount
2So refrigerating capacity also can only improve its recruitment Δ Q
2
Afterwards, vaporized low pressure gaseous coolant in evaporimeter 6, as described above, flowing through the process of gas-liquid heat exchanger 4 from refrigerant pipeline L4, be used for making from refrigerant pipeline L2 and be fed to high pressure refrigerant supercooling the gas-liquid heat exchanger 4, so the temperature of described low pressure gaseous coolant rises, in the stage in being inhaled into compressor 1, the state variation shown in the g of Fig. 2 becomes the state (pressure P shown in a
1, enthalpy i
1), and only by the heat Δ Q shown in overheated this figure
1Then, the gaseous coolant that this is overheated is compressed again by compressor 1, after, refrigerant carries out and above-mentioned same state variation repeatedly.
And, in gas-liquid heat exchange type refrigerating plant of the present invention, freeze cycle described above is carried out repeatedly, absorbing heat according to the evaporation of following the low temperature liquid refrigerant in evaporimeter 6 carries out needed freezing, the temperature of the gaseous coolant that spues from compressor 1 is detected by the temperature sensor 7 that spues, pressure by the refrigerant that has been reduced pressure by heat exchange control valve 3 after condenser 2 condensations is detected by pressure sensor 8, and these detected values can be sent to controller 10.So controller 10 based on the refrigerant temperature in the exit of the compressor 1 that is detected by the temperature sensor 7 that spues and the refrigerant pressure in the exit of the heat exchange control valve 3 that is detected by pressure sensor 8, is controlled the aperture of heat exchange control valve 3.
Specifically, if the winding number of compressor 1 reduces, the aperture of then dwindling heat exchange control valve 3 on the contrary, if the winding number of compressor 1 increases, then increases the aperture of heat exchange control valve 3.In addition, the refrigerant temperature in the exit of the compressor 1 that is detected by the temperature sensor 7 that spues, if surpass setting value, then aforementioned hot is exchanged the aperture of control valve 3, be contracted to till the value that can make refrigerant maintain the gas-liquid mixed state, described refrigerant is the refrigerant (with reference to Fig. 4) that has passed through gas-liquid heat exchanger 4 after utilizing these heat exchange control valve 3 decompressions.
When for example being installed in gas-liquid heat exchange type refrigerating plant of the present invention on the van cooler, the rotation number of the compressor 1 that is driven by engine can change according to the travel condition of van cooler.
For example, the internal circulating load of the refrigerant in the freeze cycle loop can reduce if the rotation number of compressor 1 reduces then, therefore refrigerating capacity descends, in the case, as described above, because controller 10 has dwindled the aperture of heat exchange control valve 3, so flowing through the flow velocity of the refrigerant of gas-liquid heat exchanger 4 rises, heat exchange amount increases, and according to the increase of this heat exchange amount, the minimizing that reduces the heat exchange amount in gas-liquid heat exchanger 4 that the minimizing cause refrigerant circulation causes because of winding number can be compensated, the cooling that causes because of the heat exchange amount deficiency can be suppressed bad.
Herein, the high-pressure liquid refrigerant that in condenser 2, has liquefied, the state variation when flowing through gas-liquid heat exchangers 4 and toward expansion valve 5 from heat exchange control valve 3, for example B, C, the D process with Fig. 2 represents.When turning round with the state shown in the B process, by heat exchange control valve 3, the pressure of described high-pressure liquid refrigerant is from P
2Be depressurized into P
3If the winding number of compressor 1 reduces, and then according to the reduction degree of this winding number, the aperture of heat exchange control valve 3 is dwindled, shown in the C of Fig. 2, D process, like that, the pressure of described high-pressure liquid refrigerant is decompressed to P
3', P
3" (P
3＞P
3'＞P
3"), improve and increase heat exchange amount as shown owing to flowing through the flow velocity of the refrigerant of gas-liquid heat exchanger 4, so it is bad to suppress the aforementioned cooling that causes because of the heat exchange amount deficiency.
Fig. 3 represents the relation of flow velocity (m/s) Yu the heat transfer property KA (W/K) of the refrigerant in the gas-liquid heat exchanger 4, schemes as can be known thus, and heat transfer property (heat exchange amount) KA can increase along with the increase of refrigerant flow rate.
Herein, A process in Fig. 2, expression is not used heat exchange control valve 3 and is made refrigerant in gas-liquid heat exchanger 4 after the supercooling, the process (condition) of situation about being expanded by expansion valve 5, to make refrigerant make the situation of state variation as benchmark through this process A, obtain according to simulation and to make refrigerant through each process B, C, the refrigerant flow rate when D makes state variation, the heat exchange amount in gas-liquid heat exchanger 4, and performance boost rate, obtain the result shown in the table 1.
[table 1]
As shown in Table 1, when the winding number of compressor 1 reduced, if dwindle the aperture of heat exchange control valve 3, then the flow velocity of refrigerant increased, and the heat-shift in gas-liquid heat exchanger 4 increases, result, performance boost and can improve refrigerating capacity.
On the contrary, if increase the then refrigerant circulation increase of winding number of compressor 1, because because the heat-shift in gas-liquid heat exchanger 4 too much causes the temperature rising that spues at the refrigerant in the exit of compressor 1, thereby the problem of the deteriorated grade of refrigerator oil occurs, therefore, as described above, controller 10 so that the mode that the aperture of heat exchange control valve 3 increases control.
For example, when turning round under with the state shown in the D process of Fig. 2, by heat exchange control valve 3, the pressure of described high-pressure liquid refrigerant is from P
2Be depressurized into P
3", if the winding number of compressor 1 increases, then according to the increase degree of this winding number, the aperture of heat exchange control valve 3 is increased, shown in the C of Fig. 2, B process, the pressure of described high-pressure liquid refrigerant is decompressed to P
3', P
3(P
3"＜P
3'＜P
3) words, reduce heat exchange amount as shown owing to flowing through the flow velocity reduction of the refrigerant in the gas-liquid heat exchanger 4, so can suppress to rise owing to the temperature that spues at the refrigerant in the exit of compressor 1 that heat exchange amount too much causes, thereby can prevent the deteriorated of refrigeration oil.
As shown in Table 1, when the winding number of compressor 1 increased, if increase the aperture of heat exchange control valve 3, then the flow velocity of refrigerant reduced, and the heat-shift in gas-liquid heat exchanger 4 reduces, result, hydraulic performance decline and reduce refrigerating capacity.
And, in gas-liquid heat exchange type refrigerating plant of the present invention, the refrigerant temperature in the exit of the compressor 1 that is detected by the temperature sensor 7 that spues, if surpass setting value, then as described above, controller 10 is contracted to the aperture of heat exchange control valve 3 till the value that can make refrigerant maintain the gas-liquid mixed state, and described refrigerant is the refrigerant that has passed through gas-liquid heat exchanger 4 after being reduced pressure by this heat exchange control valve 3.
For example, the high-pressure liquid refrigerant that in condenser 2, has liquefied, state variation when flowing through gas-liquid heat exchanger 4 and toward expansion valve 5 from heat exchange control valve 3, for example B, C, the D process with Fig. 4 represents, if by dwindling the aperture of heat exchange control valve 3, the high-pressure liquid refrigerant that will liquefy in condenser 2 is from pressure P
2Be decompressed to significantly P
3', P
3", then can with by the refrigerant that has passed through gas-liquid heat exchanger 4 after 3 decompressions of heat exchange control valve, maintain the gas-liquid mixed state.That is, when turning round with the state shown in the B process, by heat exchange control valve 3 with the pressure of described high-pressure liquid refrigerant from P
2Be decompressed to P
3If the winding number of compressor 1 reduces, and then according to the reduction degree of this winding number, the aperture of heat exchange control valve 3 is dwindled, shown in the C of Fig. 2, D process, the pressure of described high-pressure liquid refrigerant is decompressed to P
3', P
3" (P
3"＜P
3'＜P
3), the refrigerant by having passed through gas-liquid heat exchanger 4 after 3 decompressions of heat exchange control valve maintains the gas-liquid mixed state.
As described above, by the refrigerant that has passed through gas-liquid heat exchanger 4 after 3 decompressions of heat exchange control valve, if maintain the gas-liquid mixed state, then diminish by the refrigerant of gas-liquid heat exchanger 4 and the temperature difference that is imported into via refrigerant pipeline L4 between the gaseous coolant the gas-liquid heat exchanger 4 from evaporimeter 6 with the form of gas-liquid two-phase flow, can be suppressed at than the lowland heat exchange amount of two refrigerants in the gas-liquid heat exchanger 4.Therefore, can be suppressed at than the lowland degree of superheat of refrigerant of the porch of compressor 1, be suppressed at the rising of the temperature that spues of refrigerant in the exit of compressor 1, thereby can prevent the deteriorated of refrigerator oil.
Herein, A process in Fig. 4, expression is not used the heat exchange control valve and is made refrigerant in gas-liquid heat exchanger 4 after the supercooling, the process of situation about being expanded by expansion valve 5, to make refrigerant make the situation of state variation as benchmark through this process A, obtain according to simulation and to make refrigerant through each process B, C, the refrigerant flow rate when D makes state variation, the heat exchange amount in gas-liquid heat exchanger 4, and performance boost rate, and obtain the result shown in the table 2.
[table 2]
As shown in Table 2, when the refrigerant temperature in the exit of the compressor 1 that is detected by the temperature sensor 7 that spues has surpassed setting value, if dwindle significantly the aperture of heat exchange control valve 3, the flow velocity of refrigerant can increase, on the other hand, can diminish by the refrigerant of gas-liquid heat exchanger 4 and the temperature difference that from evaporimeter 6 via refrigerant pipeline L4 be imported into gaseous coolant gas-liquid heat exchanger 4 between with the form of gas-liquid two-phase flow this moment, the result, can be suppressed at than the lowland heat exchange amount of two refrigerants in the gas-liquid heat exchanger 4, refrigerating capacity reduces.
Above, according to the present invention, can obtain following effect.That is, not only can suppress to follow the change of winding number of compressor 1 and the change of the refrigerating capacity that causes, and can be suppressed at the rising of the temperature that spues in the exit of compressor 1, thereby it is deteriorated to prevent that refrigerator oil from occuring.
Claims (3)
1. gas-liquid heat exchange type refrigerating plant, by refrigerant pipeline, to major general's compressor, condenser, heat exchange control valve, gas-liquid heat exchanger, expansion valve and evaporimeter, be connected in series, and consist of closed circuit refrigerant circulation circuit, the refrigerant that will be in aforementioned condenser have been reduced pressure by aforementioned hot exchange control valve after the condensation and by vaporized refrigerant in the aforementioned evaporation device carries out heat exchange and makes the respectively supercooling or overheated of each refrigerant in aforementioned gas-liquid heat exchanger, it is characterized in that:
Between the aforementioned compressor and aforementioned condenser of aforementioned refrigerant circulation circuit, the setting temperature sensor that spues, and between aforementioned hot exchange control valve and aforementioned gas-liquid heat exchanger, pressure sensor is set, and be provided with control device, described control device is controlled the aperture of aforementioned hot exchange control valve based on refrigerant temperature and the refrigerant pressure that is exported by the detected heat exchange control valve of aforementioned pressure sensor by the aforementioned detected compressor outlet of temperature sensor that spues.
2. gas-liquid heat exchange type refrigerating plant as claimed in claim 1 is characterized in that:
Aforementioned control device if the winding number of aforementioned compressor reduces the aperture of then dwindling aforementioned hot exchange control valve, if the winding number of aforementioned compressor increases, then increases the aperture of aforementioned hot exchange control valve.
3. gas-liquid heat exchange type refrigerating plant as claimed in claim 1 is characterized in that:
Aforementioned control device, if the refrigerant temperature by the aforementioned detected compressor outlet of temperature sensor that spues surpasses setting value, the aperture that then aforementioned hot is exchanged control valve is contracted to till the value that can make refrigerant maintain the gas-liquid mixed state, and described refrigerant is the refrigerant that has passed through aforementioned gas-liquid heat exchanger after being reduced pressure by this heat exchange control valve.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201110281313.5A CN102997527B (en) | 2011-09-09 | 2011-09-09 | Gas-liquid heat exchange type refrigeration device |
| HK13106527.4A HK1178965A1 (en) | 2011-09-09 | 2013-06-04 | Gas-liquid heat exchanging-type refrigerating device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201110281313.5A CN102997527B (en) | 2011-09-09 | 2011-09-09 | Gas-liquid heat exchange type refrigeration device |
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| CN102997527B CN102997527B (en) | 2016-03-23 |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104819590A (en) * | 2014-02-03 | 2015-08-05 | 东普雷股份有限公司 | Refrigeration device and operation method of refrigeration device |
| CN106766296A (en) * | 2016-12-20 | 2017-05-31 | 中山阿瑞德电器设备有限公司 | A kind of heat exchange cooling system |
| CN106766482A (en) * | 2016-12-20 | 2017-05-31 | 中山阿瑞德电器设备有限公司 | A kind of reach in freezer |
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-
2013
- 2013-06-04 HK HK13106527.4A patent/HK1178965A1/en not_active IP Right Cessation
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| JP2002130856A (en) * | 2000-10-23 | 2002-05-09 | Matsushita Seiko Co Ltd | Refrigerating cycle device and control method thereof |
| JP2002130849A (en) * | 2000-10-30 | 2002-05-09 | Calsonic Kansei Corp | Cooling cycle and its control method |
| JP2005351537A (en) * | 2004-06-10 | 2005-12-22 | Matsushita Electric Ind Co Ltd | Refrigerating cycle system and its control method |
| JP2007101069A (en) * | 2005-10-05 | 2007-04-19 | Mitsubishi Electric Corp | Air conditioner |
| CN200982764Y (en) * | 2006-12-09 | 2007-11-28 | 奇瑞汽车有限公司 | Automobile air conditioner |
| JP2009092258A (en) * | 2007-10-04 | 2009-04-30 | Panasonic Corp | Refrigerating cycle device |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104819590A (en) * | 2014-02-03 | 2015-08-05 | 东普雷股份有限公司 | Refrigeration device and operation method of refrigeration device |
| CN104819590B (en) * | 2014-02-03 | 2019-10-25 | 东普雷股份有限公司 | The method of operation of refrigerating plant and refrigerating plant |
| TWI709723B (en) * | 2014-02-03 | 2020-11-11 | 日商東普雷股份有限公司 | Refrigeration device and operation method of refrigeration device |
| CN106766296A (en) * | 2016-12-20 | 2017-05-31 | 中山阿瑞德电器设备有限公司 | A kind of heat exchange cooling system |
| CN106766482A (en) * | 2016-12-20 | 2017-05-31 | 中山阿瑞德电器设备有限公司 | A kind of reach in freezer |
Also Published As
| Publication number | Publication date |
|---|---|
| HK1178965A1 (en) | 2013-09-19 |
| CN102997527B (en) | 2016-03-23 |
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